High-pressure pump liner and packing



s sheets-sheet 1V A. L. LEMAN HIGH-PRESSURE PUMP LINER AND PACKING yOct. 14, 1958 Filed Jan. ll. 1955 R. E w I l om F n.v Hm /////M/ /a m//\/\//.r//////// N mmwv mm. om. QJ

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I ARTHUR L. LEMAN eYwwffjM/l/Mf Oct. 14, 1958 A. L. LEMAN 2,856,249

HIGH-PRESSURE PUMP LINER AND PACKING Filed Jan. ll, 1955 5 Sheets-Sheet2 1 1e 33 3, 45 l2o [F IG. 3 r so 3 NN 3. 3 3

Oct. I4, 1958 LEMAN 2,856,249

HIGH-PRESSURE PUMP LINER AND PACKING Filed Jan. 11, 1955 3 sheetheet 3United States Patent() HIGH-Panasonic PUMP UNER AND PACKlNG Arthur L.Leman, Houston, Tex., assignor to Maquinaria petrolifera, S. A., Crosby,Tex., a corporation of Panama Application January` i1, 195s, serial No.481,082 ii Claims. (Ci. 309-3) My present invention relates toreciprocating pumps such as those known in the oil eld as slush pumps.It aims to provide an improved cylinder and liner assembly for suchpumps including novel packing means in an interspace between thellinerand cylinder and correlated with them to withstand the increasingly highfluid pressures now employed in oil field and other pumping operations.

Heretofore and until the advent of high iluid pressures the customarysleeve packing for pump cylinder liners has served with reasonablesatisfaction. Examples of such standard liner packing are seen in myprior Patents 2,640,-`

434 and 2,686,090. More recently pump pressures have substantiallyincreased, along with reduction in size of the liner bore, until theload on the usual liner packing has exceeded the tensile strength of theconstituent rubber.

It will be evident that reduced-bore liners create loading on the linerpacking in the ratio of the cross-sectional annular. areas of the linerto the packing. For example, with a in. bore liner having 9% in. O.,D. x8% in. I. D. liner packing, l000 lb. sq. in. fluid pressure would buildup 3680 lb. sq. in. pressure in the line packing rubber.

Since pump fluid pressures now commonly exceed 2000 lb. sq. in. and theultimate strength of conventional rubberous packing is less than 3500lb. sq. in.,` suchtprior packings, as for example those of my priorpatents mentioned,` are no longer satisfactory for the high pressurepumping operations. Deterioration or destruction of the liner packingwith resultant leakage of sandy uid at the interface of liner andcylinder has caused costly damage `to pump cylinder bodies under thecutting action of the leaking fluid on the steel.

One proposed remedy has been` to provide tell-tale holes through thecylinder wall at which leakage past the packing might be detected,thereby warning of likely damage to the pump cylinder body unless givenappro- 42,856,249 Patented Oct. 14,

i tain embodiments of the invention:

priate attention. Such expedient affords merely detection pumpingservice such as at oil wells. As will be apparent from the followingmore detailed description the inven tion proceeds upon a new principleof radially ,compressing `a rubberous or other yieldable packing annuluswhile affording it opportunity for axial flow and simultaneouslystopping or axially retaining the liner relative tothe pump cylinder by`positive direct metal-to-metal contact by-` passing and relieving thepacking from the burden of having to oppose by ,itself axial pressuresbetween the Alinerand cylinder.

Fig. 1 is a longitudinal sectional View including the head end of a pumpuid cylinder and inserted two-part liner and packing assembly typifyingthe invention;

Fig. 2 shows a portion of the pump cylinder assembly of Fig. lincludingthe packing region, upon an enlarged scale; t

Fig. 3 is a view similar to Fig. 2 showing the packing means thereof incourse of assembly with a one-piece liner; t

Fig. 4 illustrates another modification in longitudinal `section andwherein the packing and stop means built upon the outer member or shellof a two-part liner;

Fig. 5 is another modification similar to that of Fig. 4 in associationwith a one-piece liner;

Fig. 6 shows in longitudinal section a still further modication whereinthe pump cylinder body and the liner are mutually tapered at the packingregion; and

Fig. 6A corresponds to a portion of Fig. 6 with the parts in course ofassembly.

Referring now more particularly to Figs. 1 and 2, also also Fig. 3, Ihave represented in Fig. 1 sufficient of a typical pump structure tolocate and identify the elements with which the invention is primarilyconcerned. Such structure comprises a iluid cylinder 1 of areciprocating piston pump including the head end 3 thereof having afluid outlet as at 4 to a discharge valve, not shown. The cylinder hasthe conventional or other counterbore as at 5 closed as by the boltedcover plate or head 6 in which a lock-up screw 7 takes againsta spider 8bearing axially against the cylinder liner means, in this instancethrough an annular thrust bearing ring or gland 9 received on and inaxially abutting relation to the liner element.

The liner means in the example of Figs. ll and 2, also Fig. 4, is atwo-part element designated as a whole at 10. lt comprises an outercylindrical shell 11 having a portion directly received in and by theinner wall of the pump cylinder 1, and an inner sleeve 12 havingportions directly received in the shell 11. The two-part liner 11, 12 ofFigs. l and 2 represents one preferred form of liner construction, beingthat disclosed and claimed` in my previously mentioned Patent No.2,686,090. The invention however is equally applicable to other cylinderand liner constructions.

For the purposes of the invention the lluid cylinder lsuch as 1 of Fig.2 and the liner represented. by the two-v part element `10 of Figs, 1and 2 are mutually formed to provide between them an annularinterspaceor cavity for the packing and stop means to be described. Suchcavity is designated generally at 20, being in' this case adjacent thehead end` of the cylinder 1. Depending on the manufacture and design ofthe particular pump the total lcavity may comprise a number of cavityalong the cylinder.

The packing cavity such as 20 of Figs. 1 to 3 is defined between theinner wall of the counterbore portion 5 of the cylinder and the outerwall of the liner element, here the outer member or shell 11 thereof.Said elements provide for the cavity opposed longitudinal side orcircumferential Walls and opposed transverse or radial end walls, one ofthe latter at 1a on the cylinder at the inner end of the counterboreportion"`5 and the other at the inner face of a retainer ilange 11a onthe liner shell 11. As will be evident from the other figures, suchtransverse cavity walls may comprise integral portions of the fluidcylinder and of the liner or may be otherwise presented as by an elementcorresponding to the `retainer ring or gland 9 of Fig. l; see Figs. 4and 5. In any case the cavity cross walls are such as to be subject toaxial forces in one and the opposite direction in theoperation of thepump.,

In the particular example of `the two-part liner 10 of portions p Figs.y1 and 2, the gland 9 engaged by the spider 8 thrusts against an annularprojection 13 on the liner sleeve 12 and the latter at its opposite endhas longitudinal limiting abutment at a stop shoulder 14 engaging aninfacing stop shoulder 15 on the liner shell 11 whereby longitudinalcompression upon the sleeve 12 is balanced by longitudinal tension uponthe shell 11. Hence the packing cavity outer end wall 11a is under axialforce in the direction toward and resisted at the opposite or inner endwall 1a cf-.the cavity.

In cooperation with such cylinder and liner interspace or` packingcavity the invention provides packing and positive stop means such thatthe liner is positively positioned and held in the pump metal to metalagainst axial movement and the packing or seals pack oif the uidbut donot themselves retain the liner axially, being left free to flow axiallyinto space provided therefor in the cavity while attendantly beingradially compressed.

Such packing and stop means in the example of Figs. -1 and 2, andsimilarly in Fig. 3 showing a one-part liner 101, comprises a pluralityof yieldable annular packings or ring seals preferably of rubber orrubberous material correlated with longitudinally inclined wall means ator in the cavity and affording a positive metal-to-metal longitudinalstop with respect to the packing or seals. In this example the sealmeans includes a plurality of pairs 'of the yieldable annular packings,of tapered or wedgelike cross-section. Each such seal pair comprises aninner ring seal or packing ring and an outer ring seal or packing ring31. Between the inner and outer seals 30, 31 of each pair is interposeda flared or tapered metal ring 35,l herein for identification termed acone. Such cones 35 each comprises an inclined bar-like body andopposite end portions 36, 37 adapted to abut respectively an adjacentendwall 1a or 11a of the cavity and to thrust axially against each othereither directly or through interposed metal. In the example of Figs. 1and 2, or Fig. 3, such interposed metal comprises a lantern ring ttlmedial along the cavity 20 and in transverse line with an aperture ortell-tale hole opening from the liner to atmosphere through the wall ofcylinder 1. Such lantern ring may be variously constructed and arrangedto provide a path to the tell-tale hole for such, if any, leakage ofHuid as may after long wear periods or in the event of faultyconstruction or installation work past the packing i means. Asrepresented it is in the form of a metal ring of general rectangularsection having annular channels 41, 42 at the outer and innercircumferential faces and one or more of circumferentially distributedholes 43 communicating between said channels and via the outer one tothe tell-tale hole 45. Thus the cavity 10 contains the yieldable packingpairs 30, 31 at opposite sides of the tell-tale opening 45 in thedirection axially of the cylinder.

Said packings 30, 31 are adapted to be radially compressed at and by theinclined or taper surface at the cavity and in this instance presentedthrough the medium of the cones 35. Said cones 35 also provide alongitudinal stop between the liner and the uid cylinder by effectivelyinterposing a strut between the opposite end Walls of the cavity, thetotal strut in this instance including the interposed metal of lanternring 40.

A further important feature of the invention lies in the attendantshaping, dimensioning and relative positioning or arrangement of theyieldable packing members 30, 31 and the strut-forming metal andassociated inclined longitudinal wall so that packing cavity space isprovided for free elongation and longitudinal iiow of the packingr atone or the other or both longitudinal ends thereof. Such longitudinalpacking expansion space of the cavity 10 is indicated in Figs. l and 2at 32 and 33 at the narrower ends of the wedge-forming packing rings 30and 31 respectively. The latter as shown are oppositely positioned and'said expansion lcavity portions 32, 33 accordingly are at opposite endsof each packing pair.

It will be understood that the yieldable packings are so formed anddimensioned that in the initial or unstressed state ample expansionspace is provided in the cavity as at the points 32, 33 such asindicated, and that in the intalled or assembled position of Figs. 1 and2 the resultant axial elongation of the packings reduces the expansionspace accordingly, even to substantial end contact of the packings andcross Walls. But the initial spacing and dimensioning of the parts inany case is such that any objectionable axial thrust or force upon thepacking is relieved and shunted or by-passed through or around thepacking by the direct metal-to-metal abutment and 'strut-like action ofthe described metal parts, leaving the packing to assume no materialpart of the burden of opposing axial forces between the liner and thecylinder.

The manner of installation and operating principles concerned arefurther iilustrated in the embodiment of Pig. 3. There the packings 30,31, the cone elements 35 and general. dimensioning and arrangementthereof in the fluid cylinder 1 are similar as in Figs. 1 and2. The Fig.3 example differs mainly in that the cylinder liner 101 is a one-partcylindrical element including an integral ian'ge 1.01ct presenting anend wall for the cavity 20. In the process of assembly one inner ringseal or packing ring 30, one cone 35, the lantern ring 40 and bothoutei` packing rings 3i are set into the packing cavity 20 of the pumpbody. The packings and cones may be preparatorily lightly greased andfor easy entrance the inner seal 30 should be but lightly placed in thecone 35. The other inner packing ring 30 and the associated cone 35 areplaced on the liner 101 as seen at the right in Fig. 3, the liner andpacking desirably being greased. The liner 101 is then fully insertedinto the cylinder 1 and set up tightly as by turning up a lock-up screwlike 7 of Fig. 1, this being followed by -retightening after a briefperiod of operation of the pump, say 30 minutes. In this manner theliner is set up tightly in complete metalto-metal longitudinalforce-bearing relation to the pump Huid cylinder 1. At the same time thepacking is relieved of axial stress and left free to flow longitudinallyat the expansion zones 32, 33 through the medium of the described strutaction of the metal parts and while receiving radial compression underthe action of the tapered surface. l

In Figs. 4 and 5 I have represented modifications wherein the packingand the longitudinal stop means are in effect built onto the liner inlieu of separately assembled parts such as the cones 35 and 35a of theprevious figures. In Fig. 4 the pump cylinder 1D and the insert linercomprising an outer shell 111 and inner sleeve 112 are mutually formedto present an annular packing cavity designated as a whole at 120. Inthis instance an outer end wall of the cavity is provided by retainerring means 109 having endwise engagement with both parts 111 and 112 ofthe liner as at 10961, 109b and engaged at its outer portion by thelock-up means such as the head spider 108.

The inclined longitudinal wall means at and in the cavity is in thisexample of Fig. 4 formed on and provided by an annular projection orcollar designated as a whole at 135, integrally or otherwise located onthe outer wall of the liner, in this case on the liner shell 111. Itincludes at opposite end portions oppositely inclined longitudinal walls136, 137 radially spaced from the opposite longitudinal wall portion ofthe cylinder 1D to provide therewith packing cavity portions' 1,20a,120b together constituting the entire packing cavity 120. Yieldablepacking rings 130, 131 are disposed in the respective cavity portions136, 137.

Here again said packings or sealing annuli 130, 131 arecross-sectionally shaped and proportioned so that when assembled theyare placed under radial compression at and by the respective inclinedsurfaces 136, 137 but are left with capacity for free axial elongationby reason of expansion spaces or zones such as 132, 133 in the cavity atone or both ends of the respective packings. As in the previous forms anopening to atmosphere from the liner is alorded at the region of thepacking cavity such as the tell-tale hole 45 in line with a medialcircumferential channel 138 on the liner shell 111 intermediate theplural packing cavity portions 136, 137. It will be seen in Fig. 4 thatthe collar 135 of the liner serves to present inclined longitudinal wallmeans coactive with the packing to place it under radial compression andthat the parts are relatively dimensioned to alord axial expansion spacefor the packing, said wall means simultaneously posing a longitudinalstrut affording a positive stop as between the liner and the cylinderand relieving the packing of excessive axial thrust.

The embodiment of Fig. 5 is similar to that of Fig. 4 but shows a singleor one-part liner 210 for the cylinder 1E. Corresponding parts' in Fig.5 are similarly num bered as in Fig. 4 raised by 100.

Figs. 6 and 6A illustrate another modilication including the pumpcylinder 1F and an insert liner 310 shown as a one-piece element butwhich may comprise two or more concentric cylindrical members. 'Iheliner 310 is locked up `and retained at the head endtas by the usualspider 308. In this instance the annular packing cavity between thecylinder and liner is defined circumferentially by inclined longitudinalwalls 321 and 322 formed respectively at the inner wall of the bore ofthe cylinder 1F and at an opposed portion, in the assembled Fig. 6position, of the insert liner 310. In other words, the cylinder and theliner are provided with radially opposed and generally conformantlongitudinal wall portions 321 and 322 tapered or inclined relative tothe cylinder axis. Transverse walls for the packing cavity 320 may beprovided either on the cylinder or on the liner or partly on each, beingshown on the liner 310, the latter being circumferentially channeled topresent cavity transverse end walls 323, 324 and also intermediatetransverse walls 325, 326 for the respective cavity portions. Therespective portions of the cavity 320 each receive a rubberous or otheryieldable packing ring 330, 331, in this instance shown as ofsubstantially rectangular cross-section.

As best seen in Fig. 6A with the cylinder and liner at an intermediatestage of installation the cavity or cavity portions 320 and theyieldable packings 330, 331 are shaped and relatively proportioned sothat in the initial unstressed state the packing exceeds in radialdimension that of the cavity and is lesser in axial dimension than thecavity to provide axial expansion zones as at 332, 333 at one or theother or both longitudinal extremities of the packing. By comparison ofFig. 6A with Fig. 6 it will be seen that under full insertion andlocking up of the liner 310 into the cylinder 1F the packing rings 330,331 are by reason of the inclined longitudinal wall means of thecylinder and liner placed under radial compression with attendant axialelongation and with the longitudinal wall means of the liner serving instrut fashion to provide with the opposed wall portion of the cylinder apositive metal-to-metal stop preventing longitudinal.

stress from being effective upon the packing. As in the previousembodiments communication from the liner to atmosphere preferably isprovided at the region of the packing cavity such as' the tell-tale hole45 disposed between the packing members and communicating with acircumferential groove 335 on the liner substantially medial of the ofthe packing cavity 320. Thus the yieldable packings 330, 331 aredisposed at opposite longitudinal sides of the opening 45 to atmosphere.

It will be understood that for the high-pressure pumping operations withwhich the means of my invention is particularly useful the yieldabl-epackings or seal rings such as 30, 31 of Figs. l to 3, 136, 137 and 236,237 of Figs. 4 and 5, or 330, 331 of Fig. 6, of rubber, rubberous orother material adapted to yield radially and flow or elongate axiallyunder the high pressures concerned may be comparatively dense and moreor less solid 1n body giving them a self-sustaining or semi-rigidcharacter such that the radial compressibility and axial flow capacityunder the described installation may not readily be evident underordinary handling prior to installation. For similar reasons thecross-sectional shapes of the packings may be considerably varied withinthe mentioned requirements of provision for radial compression and axialelongation. Hence, depending on the pressures and other operatingcircumstances and the particular make or design of pump for which thecylinder and liner assembly of the invention is intended, the packingsmay be in the unstressed state and as -to any of the exemplaryembodiments be of substantially rectangular cross-section as in Fig. 6or of a more or less tapered or wedge-form so long as they are adapted`for coaction with the inclined longitudinal wall or surface means ofthe packing cavity and to be subject to radial compression and axialelongation therein as in the manner herein disclosed.

My invention is not limited to the particular embodiments thereofillustrated and described herein, and I set forth its scope in myfollowing claims.

I claim:

l. For a reciprocating pump, an assembly comprising a cylinder and aliner concentric therein, the cylinder having a lateral :opening to theatmosphere, the cylinder and liner having an annular packing cavitydelined between them lon each side of the cylinder opening, a yieldableannular elastomeric packing in each cavity, each cavity havinglongitudinal wall structure presenting radially opposed longitudinallyextensive circumferential surfaces of which at least one is disposed ata small angle to the cylinder axis whereby axial thrust forces on theliner impart radial compression to the packing, each cavity havingaxially opposed transverse end wall structure predeterminedly spaced toprovide cavity space for axial movement and flow of the packing underradial compression thereof, such end wall structure at the opposite endsof the respective cavities being subject to opposed abuttivelongitudinal `thrust effective on the packing in adjustment of the linerto the cylinder, and said longitudinal wall structure defining ametallic strut for directly assuming axial thrust forces on the linerand relieving the packing of the same up to the maximum expectable inthe assembly and operation 'of the given pump.

2. A reciprocating pump cylinder and liner assembly comprising anaxially elongate packing cavity between the cylinder and liner,yieldable annular non-metallic packing in the cavity, and metal means atthe cavity presenting a longitudinally extensive wall inclined at asmall angle to the cylinder axis, said wall disposed radially oppositethe packing and placing the latter in radial compression and posing astrut relieving the packing of axial forces as between the cylinder andliner, the

cavity havingtransverse end walls subject to opposed abuttive thrust ofsaid axial forces effective on the packing as limited by said relievingstrut action.

3. A reciprocating pump cylinder and liner assembly according to claim 2wherein the longitudinally inclined wall is integrally formed on one ofthe assembly parts comprising the cylinder and liner.

4. A reciprocating pump cylinder and liner assembly according to claim 2wherein the longitudinally inclined wall is integrally formed on theliner.

5. In a reciprocating pump, a fluid cylinder dening an axis, a removableliner, a packing cavity between the cylinder and liner, an opening inthe cavity from liner to atmosphere, the cavity containing at oppositeaxial sides of the opening a longitudinally extensive metal wall membertapering axially of the cylinder at an acute angle to the axis thereofand posing a strut between the cavity ends, and yieldable annularelastomeric packings radially opposite said Wall members withlongitudinal expansion `zones in the cavity at an end of each packing,the pack- 7 ings being radially compressed at the tapering wall meinbersand being free to elongate axially by reason of a positive stopmaintained by said strut, the cavities further .defined by transverseend wall structure imposing radially compressive axial thrust yon thepackings up to limitation thereof by the strut action.

6. In a reciprocating pump having a cylinder and a cylinder linerconcentrically receivable therein, the opposed walls of the cylinder andliner mutually formed to present between them an annular packing cavitywith l-ongitudinal and transverse metal walls including longitudinalwall means inclined at an acute angle of markedly less than 45 to thecylinder axis, and yieldable annular packing of initial unstressed formand dimension to receive under opposed axial thrust 'forces as betweenthc cylinder and liner on installation in the cavity radial compressionat the inclined wall means and axial elongation toward the cavity endwalls, said cavity walls simultaneously affording a positive metallicstop as between the cavity end walls.

7. In a pump cylinder and liner assembly comprising in combination withthe cylinder bore a cylindrical liner for reception therein, the linerand cylinder bore mutually formed to define between them an annularcavity presenting radially disposed transversed walls and longitudinalcircumferential outer and inner walls, the latter including a wallportion inclined at -a small angle to the cylinder axis, and yieldableannular'packing in the cavity and of elongate and angularcross-sectional shape and dimensioned relative thereto to provide forfree axial ow of lthe packing under radial compression thereof by aWedging action at the inclinedwall portion, said walls adapted to limitsaid packing wedging action by affording direct inetal-to-metal abutmentpositive shunting relief to the packing as against axial thrust betweenthe cylinder and liner.

8. In a reciprocating piston pump having a uid cylinder and a removableliner including wall means defining an annular packing cavity between--the liner and cylinder, an opening inthe cylinder from said cavity toatmosphere, said wall means including at opposite sides of the openingacutely longitudinally tapered surfaces, yieldable annular packing atthe respective sides of the opening and initially shaped and dimensionedcross-sectionally relative to the cavity to afford the packing freedomto elongate axially and adapting it to be radially compressed betweenthe tapered surface and a radially opposite wall of the chamber, opposed-transverse end wall means for the cavity adapted to effect such radialpacking compression by axial thrust thereon as between the liner and thefluid cylinder, and positive stop means to limit said axial thrust.

9. A reciprocating pump cylinder and'liner assembly according to claiml2 wherein the longitudinally inclined wall is on a cone assembled intothe cavity.

l0. A reciprocating pump cylinder and liner assembly according to claim2 wherein the longitudinally inclined have radially opposed axiallytapering wall portions deiining longitudinal walls of the cavity.

ll. In a reciprocating piston pump according to claim 8, theconstruction wherein the inner wall of the cylinder andthe outer wall ofthe liner are conformantly tapered at the packing region.

References Cited in the le of this patent UNITED STATES PATENTS2,584,518 Walton Feb. 5, 1952 2,650,868 Waldron Sept. l, 1953 FOREIGNPATENTS 27,378 Great Britain Oct. 2l, 1899 632,173 Germany July 3, 1936

